Calculating mechanism



Aug. 18, 1953 c. A. PARKER 2,649,250

' CALCULATING MECHANISM Filed Sept. 15, 1949 s Sheets-Sheet 1 IN V EN TOR. Charles /9. Parker HTTOANEK Aug. 18, 1953 c. A. PARKER CALCULATING MECHANISM 5 Sheets-Sheet 2 Filed Sept. 15, 1949 IN V EN TOR.

BY Char/e5 fl Par fer c. A. PARKER CALCULATING MECHANISM Aug. 18, 1953 s Sheet s-Sheet :5

Filed Sept. 15, 1949 HTORNEY.

us- 18, 1953 c. A. PARKER CALCULATING MECHANISM 5 Sheets-Sheet 4 Filed Sept. 15, 1949 INVENTOR. Charles .I. l d/fer Aug. 18, 1953 c. A. PARKER CALCULATING MECHANISM 5 Sheets-Sheet 5 0 lie 2 Filed Sept. 15 1949 5,0501 recqzled IN V EN TOR. Charles J! Pan [fer fiat rented Aug. 1 8, 195;?

UNITED STATES PATENT OFFICE.

CALCULATING MECHANISM Charles A. Parker, Knoxville, Tenn., assignor to Rainey Accounting Machine Company, Inc., Knoxville, Tenn., a corporation of Tennessee Application September 15, 1949, Serial No. 115,926

24 Claims. 1

This invention relates to calculating machines in Which register pinions are shiftable into and from mesh with calculating actuator racks for calculating and total taking operations, and wherein the tens transfer is accomplished by an additional step movement of the actuator rack. An operating member movable at each actuation through a cycle between two limit positions, in one of which it is at rest, powers stroke movement of the racks and the pinion shifting means; and there is reset mechanism for restoring to normal limit position, in the first part of each cycle of the operating member, all those racks and rack rests moved from that position in effecting transfers during the preceding cycle.

Customarily in such machines, the pinions remain in mesh at the end of each calculating stroke of the racks when the operating member comes to its position of rest at the end of its cycle. At this stage, when a transfer has been effected, one or more racks and their rests may be held out of their normal limit positions. As the reset mechanism is not actuated until the following cycle of the operating member, it is necessary in most types of machines to effect one or more blank cycles of the operating member to disengage the pinions, reset the racks and rack rests, and reengage the pinions, before a total can be taken. Elimination of enforced blank cycling has long been desired; a practical solution of the problem appears to have been reached in this invention.

Any reset mechanism of the character indicated encounters resistance which increases in magnitude from a minimum at start to a maximum at conclusion. It is required to return the racks against the force of springs which bias the racks to move into transfer receiving position. It must also return the rack rests to initial position. As the rests cannot return at a rate of movement faster than their corresponding racks, the load in moving the rests, which usually have independent bias, is added to the load imposed by return of the racks. Furthermore, the load imposes maximum resistance in the first half cycle movement of the operating member. In moving through the first half of its cycle the operating member provides the motive force for advancing the calculating actuators and their racks and for elevating type bars to printing position; all of which is against spring bias that increases in magnitude as the operating member nears the end of its first half cycle. The operating member is thus subjected to a heavy load in 2 the first part of its cycle at the very time that minimum load is most desirable.

Any reset mechanism that can be fully operated independently of the cycling operating member eliminates the need of blank cycling but is subject to the same resistance conditions encountered as when it is actuated by the operating member. The prior art has evolved spring powered means for operating the reset mechanism independently of the operating member by actuation of the total key, thus eliminating enforced blank cycling; but in all such cases the maximum effective power of the spring is exerted at the start of reset operation, when resistance of load is at the minimum; and when peak load is reached, at which time maximum spring power could best be utilized, the effective power of the spring is weakest. Maximum efiiciency requires maximum spring power at maximum load, but the prior art has not shown how this can be ac complished.

In machines which operate the reset mechanism independently of the main operating member and under actuation from the total key, an objectionable characteristic is liability to incomplete operation. When an operator of the machine inadvertently pushes the total key, even though the error be caught immediately and the key be not fully moved, the mechanism has to some degree already been set in operation and, unless the proper time interval is allowed, there is likelihood of jamming or improper machine functioning and breakage of parts.

Another feature which seems to have been overlooked in prior art eiforts deals with balanced operation of the mechanism. It is highly desirable that the machine function at all times with a smooth, even working of its parts. Reset mechanisms that are arranged for actuation independently of the machines main operating member must, in the interest of eiilciency, designed to operate in as smooth a manner as that at which they operate when under the control of the operating member.

An object of the invention is to provide, in a calculating machine wherein racks and their rests are moved from normal position in effecting transfers, an improved reset mechanism for returning the parts to normal position prior to taking a total, simply by actuation of the total key; wherein the reset mechanism functions automatically by the power of spring means made efiective upon the removal of a holding condition normally imposed by a movable element of the machine when the machine is at rest.

Another object is to provide, in a calculating machine having a cycling operating member and reset mechanism, power means biased to operate the reset mechanism independently of the operating member, in conjunction with limiting means movable with the operating member to regulate the speed at which the reset mechanism operates when the machine is cycled.

A further object is to provide, in a calculating machine having a reset mechanism operated normally during each cycle of the machine, means operative from the total or subtotal key to effect operation of the reset mechanism while the machine is at rest prior to .cycling, in conjunction with mechanism actuated by cycling of the machine for restoring the reset mechanism to initial condition during the conclusion of each cycle.

Still another object is to provide an improved reset mechanism for restoring the racks and rack rests of a calculating machine to normal position following transfers between racks, wherein either of two restore members adapted for joint operation in unison is capable of effecting rack reset if its operation be faster than the other.

It is also an object to provide spring powered reset mechanism in which the power of a cycling operating member, moving in the second half of its cycle, is employed to energize the springs by which the reset mechanism is operated.

Other objects will be apparent from the following description in conjunction with the accompanying drawings.

In the drawings:

Fig. 1 is an elevation of the rear right hand side of a machine in which the apparatus of this invention is incorporated;

Fig. 2 is an elevation similar to Fig. l, but with parts of Fig. 1 removed and with other parts, that are not shown in Fig. 1, added;

Fig. 3 is substantially a top plan view of the control means for actuating the reset mechanism, shown in normal position;

Fig. 4 is a plan view similar to Fig. 3, with the parts shown in actuated position;

Fig. 5 is a fragmentary elevation showing details of th racks and rack rests following a trans fer between racks and with the reset mechanism in position prior to operation;

Fig. 5A is a fragmentary elevation illustrating detail of the connection between a rack and its actuator slide at the front end of the rack.

Fig. 6 is a view similar to Fig. 5, but illustrating the same parts with the reset mechanism fully operated to return the racks and rack rests to normal non-transfer-receiving position;

Fig. 7 is a vertical section through an element of the reset actuator means;

Fig. 8 is a fragmentary elevation of the structure shown in Fig. 7, but rotated ninety degrees relative thereto;

Fig. 9 is a schematic view illustrating phases of operation of the power means by which the reset mechanism is actuated.

As herein disclosed, the invention is incorporated in a calculating machine of the type shown and described in the application of Charles A. Parker, Serial No. 109,570, filed-August 10, 1949, but it is not intended that it be restricted thereto. The invention is designed to function in any calculating machine that embodies actuator racks normally held by individual rests in a nontransfer-receiving position at the conclusion of a calculating operation that does not involve a transfer, and wherein the racks arespring biased to move to transfer-receiving position. When a transfer is effected the racks receiving a transfer are given additional movement, whereby they are held in transfer-receiving position. The mechanism for resetting the racks and the rack rests normally is controlled from the operating member of the machine, and means is provided for operating the reset mechanism independently of the operating member for the purposes of total taking without the necessity of an enforced blank cycle.

As shown, the machine includes a calculating unit C, sometimes referred to as a register section, disposed between parallel side walls M! of the calculating unit frame. These walls are secured to the base B of the machine and extend longitudinally in rear of the usual carriage, platen, and type bar assembly. The type bars are lifted to and from platen printing position, as in usual practice, by actuator slides A that move between two limit positions under the power of a main operating member OP which moves through a cycle either revolving or reciprocating. In this instance the operating member is only partly shown. The illustrated portion comprises a transverse bar at the rear end of a reciprocable frame which is driven through the agency of clutch-engaged motor means, not shown. Each actuation of the operating member effects its travel from its rearmost limit position, as shown in Figs. 1 and 4, forwardly to a limit position indicated in dotted lines in Fig. 4, and then back to its normal rest position at the conclusion of its cycle. In the normal course of operation of the machine during a calculating operation involving addition or subtraction, the register pinions are shifted to and from mesh with the racks by a driving connection with the operating member. This driving connection is herein only partly shown, as its principal components do not comprise a part of this invention. Any suitable mechanism may be employed. That portion which is here shown includes a vertical rocker post 2t that is fulcrumed intermediate its ends to oscillate in a vertical plane on a pivot stud 25 secured to a vertical support plate S appropriately fixed to the base of the machine at the right hand side of the calculating unit and in lateral spaced relation therefrom. Above its fulcrum point, the rocker post has a pivotal connection 25 with the forward end of a lever 2-? which extends horizontally rearward and terminates at its rear end in an enlarged T-head 28. The arms of the head are formed with end opening keeper slots adapted to ride over and engage either of a pair of diametrically opposed studs 39 and 35 that are secured to a connector disc 29 that is mounted for rotation on an element of the calculating frame side wall 418.

The calculating machine in which this disclosed embodiment of the invention is incorporated has a dual register comprising an upper set of register pinions tit and a similar lower set of pinions 64. These pinions are adapted to be shifted in relation to upper and lower rack: sets it. These racks include toothed upper bars it and lower bars fl, and are adapted for reciprocation in their respective horizontal planes by the stroke action of the actuator slides with which they are associated. The connector disc 29 has pivotal connection with a pair of oppositely directed links 33. These links at their outer endssupport the sets of register pinions {for bodily shifting in accordance with the throw of the links when actuated from the connector disc 29.

As illustrated in Fig. 2, the register pinions are shown in mesh with the add bars of their respective racks at the conclusion of an addition operation of the machine, wherein the racks and the operating member are in their rear positions with the operating member at rest at the conclusion of the cycle. In the normal course of add and subtract operation, when the motor clutch is engaged to cycle the operating member, the operating member moves forward and rocks the post 2 2 for a corresponding actuation of the lever 2'! to rotate the connector disc 29. Movement of this disc carries the register pinions out of engagement with their respective racks, and they remain disengaged during the remainder of the first half of the cycle at which time the racks are differentially positioned corresponding to items indexed in the machine. Prior to return movement of the racks coincident with the second half cycle movement of the op erating member, the register pinions are shifted into engagement with their respective racks so that the entered item is added or subtracted in the calculating unit in accordance with the machine controls. When the racks arrive at the end of their calculating stroke they engage rests which hold them either in a normal non-transfer-receiving position or in a transfer-receiving position, depending upon the establishment of transfers during the calculating stroke. Each rack is spring urged to move rearwardly for a further movement necessary to receive a transfer.

The rack rests of both register sets comprise thin planar rockers 82 pivoted freely on a fulcrum shaft 83 common thereto which extends transversely between supports secured on the calculating unit side walls 40. As best shown in Figs. 5 and 6, the rack engaging edge of each rocker has a relatively long straight edge face portion 84 and a short straight edge face portion 85 at an obtuse angle rearwardly from the portion 84. Both portions are tangential to the arc of swing of the rocker. Normally, with the racks at rest in rearmost position under conditions of no transfer in the register, the rockers are disposed with their short edges 85 engaged by the racks. The rockers of the respective register sets are relatively reversed, with the fulcrum shaft 83 in the upper register horizontally aligned with the bottom rack bars I1, and with the fulcrum shaft in the lower register horizontally aligned with the top rack bars 76. In each case the short edges 85 of the rockers are horizontally oflfset relative to the fulcrum point, so that pressure of the engaged racks under the rearward urge of their biasing springs 19 constantly biases the rockers to pivot in a direction to bring their long edges 84 to rack holding position. The rests 82 normally are held against such pivotal movement by a latch lever 85 individual to each rocker directly in rear thereof. The latch levers in each register set have one end freely pivoted on a fulcrum shaft 8'! common thereto and extending transversely between the supports which mount the rocker shaft. A recess in the forward edge of each lever provides a shoulder 88 that engages over a nose 89 on the adjacent rocker when the latch lever is disposed vertically in parallel relation to the rear end of the associated rack. The end of the nose 89 is rounded off to provide ample clearance in the latch lever recess, and the latch shoulder 88 is so located that when it is engaged over the nose of the rocker the nose outwardly of the side walls.

is held in the same horizontally offset relation to the. rocker fulcrum point as the short edge 85 of the rocker. Due to this arrangement, the pivotal bias of the rocker is transmitted through its nose portion as a vertical longitudinal thrust against the latch shoulder 88, so that the latch is held forcibly engaged also under the urge of the springs 19 when the rack contacts the rest. A relatively weak contractile spring connected between the rocker and the latch lever near its fulcrum point maintains the lever in contact with the rounded edge of the rocker nose when the latch is disengaged and serves also to bias the nose of the rocker for movement out of a position in which it can engage the latch lever shoulder 88.

Fig. 5 illustrates the position of the racks and rests in a pair of adjacent racks at the conclusion of a calculating stroke in which a transfer has been effected. The transfer mechanism, which forms no part of the present invention, involves a tripping of individual latches 86. When the latch of any rack rest is tripped, the rack moves to the position indicated in Fig. 5, with its associated rest swung to present its face portion 84 for rack engagement. As the face 84 is disposed at a lesser radial distance from the fulcrum than is the short face 85, it follows that the transferreceiving rack will be permitted a one-step further movement beyond the transferring rack, as shown. This condition continues until the racks and their rests are reset, at which time the parts assume the position shown in Fig. 6, with the rear ends of all racks engaged against the short face portions 85 of their respective rests.

When the operating member is cycled for another computing operation the register pinions are shifted to neutral disengaged position intermediate the rack bars-at the beginning of the cycle and then resetting means is motivated to restore and relatch all rack rest rockers pivoted out of initial position in effecting transfers. The reset mechanism includes a fulcrum shaft I00 supported in and transversely between the side walls iii? of the calculating unit frame in both registers. The opposite ends of these shafts project outwardly through the walls All. A vertically disposed lever I0! is pivoted intermediate its ends on each projecting end of the fulcrum shafts In conformity with the offset relation of the upper and lower registers, the levers iEl are correspondingly offset and are connected at their inner ends by a link I62 for movement in unison. Oscillation of the levers llll i normally effected by means of a throw link I83 which is pivotally connected at its rear end to a cross bar I64 connected transverse- 1y between the outer end portions H35 of the levers H3! in the lower register. A second lever I08 is pivoted at its outer end on the fulcrum shaft let for oscillation alongside each lever 10!. These levers Hi5 are inclined forwardly with respect to the levers NH, and each pair supports between its inner ends a transverse reset bar I01 which plays freely through clearance apertures I68 in the walls 48 forwardly of the rack rest rockers 82. A coiled contractile spring N39 is trained over a sheave H8 on the inner end of each lever lfil of the lower register and yieldingly connects the inner ends of the levers E56 and shafts H! for movement in unison. When the levers Hll are rocked by pull of the link 503 as the operating member moves forwardly, the sheave H8 pulls the spring I09 rearwardly andcorrespondingly rocks the levers I06 I to move the reset bars I01 against the outer front ends of the rockers 82 and return them to initial latched position.

Rack reset means is provided for operation in conjunction with the rocker reset mechanism. The rack reset in each register includes a third lever III also pivoted on the fulcrum shaft Illi! alongside each lever I536 to oscillate in a vertical plane. The levers I I I mount between each pair a transverse reset bar IIZ which plays freely through clearance apertures H3 in the walls 40 in rear of the racks. When the actuator levers IiiI are rocked, the levers III are correspondingly pivoted through the pull of a contractile spring IM connected between one end of each lever II I and the cross bar IIM in the lower register set, and between one end of each lever III and the free end of an auxiliary link H5 in the upper register set. The other end of each link I I5 is pivotally connected to the forward end of the link I02. By means of the linkage just described the rack reset bars II2 engage the rear ends of those racks moved transferringly beyond the others and restore them to initial alignment with the others. Further forward propulsion of the racks is prevented by engagement of the bars II2 against the forward ends of their clearance apertures II3, which ends are vertically aligned with the short edges 8-5 of the rests 82 when in initial non-transfer position.

Resetting of the racks is expedited by the camming action of the rests 82 against the rear ends of the racks as the rests are swung by their own reset bars I07, Furthermore, when the rests begin resetting movement, their nose portions 89 move away from the latch levers which already are spring biased to move into engaged position; so that when the rests cease their swing the latch levers continue to move until their shoulders 88 are fully latched over the noses of the rests.

The restoring bars IOI and H2 of the reset mechanism travel through arcs in the direction of the arrows in Figures 5 and 6. It will be noted that the major portion of the travel of each bar III'I- takes place as the bar is moving rearwardly to engage those rests which have been tripped out of their normal position in effecting transfers. This portion of the travel is at a relatively rapid rate, and when the bar engages the tripped rests its movement decelerates in proportion to the load imposed by the resistance of the rests in returning to normal position. It is, therefore, highly important to smooth, fast operation that maximum power be applied to the reset mechanism in that period when the reset bars encounter their maximum resistance. bars II2 are moved forwardly into contact with the racks to provide a forward propulsion which returns the racks to normal non-transfer receiving position against the bias of the rack springs, just before the bars IIII have moved the rests to their fully restored position. The force of this bias increases in magnitude with forward travel of the racks, so that it is also necessary that increased power be exerted by the reset mechanism when the bars I-I2 encountertheir maximum resistance.

In order to provide the desired increase in power, this invention includes spring motor means in combination with a system of leverage that includes a horizontal power lever I disposed transversely beneath the under part of the calculating unitside walls 40. The left hand end of the power lever is pivoted at. I2 I- on a fulcrum The reset stud carried by the base plate of the machine, so that the lever is adapted for oscillation in a horizontal plane. In. the normal position of the parts, prior to actuation of the reset mechanism, the power lever is angled rearwardly to dispose its free end beneath the operating member when the operating member is in its rearmost position of rest. Intermediate its ends the power lever has a pin and slot pivot connection I22 with the forward end of a tractor link I 23 which, at its rear end, has pivotal connection with a yoke I24 that is, in turn, pivotally mounted over a bolt I25 passed transversely between the convergent. forward end portions of a pair of arms which comprise the throw link I03. The yoke I24 provides av flexible connection which permits limited horizontal as well as vertical swing of the tractor link with respect to the power lever and the throw link. A battery of contractile springs I28 is connected at one end to an anchor element I29 fixed on the support plate S and at its other end to the free end of a lever I30 which has a pivotal connection I3I at its other end with a portion of the power lever I20 intermediate its fulcrum and its point of attachment I22 to the tractor link. The lever I30 has a pivotal connection I32 with the free end of a shiftable fulcrum member I33 that has pivotal connection I34 at its other end to the base plate B of the machine. The pivot I32 connecting the lever I30 and. the shiftable fulcrum member I33 is located adjacent the free end of the lever 13o, slightly inwardly of the battery of springs. The pivot I35 for the shiftable fulcrum member is disposed rearwardly of this point in a longitudinal direction with respect to the calculating unit, so that the parts normally assume. the position shown in Fig. 3, with the battery of springs I28 extended to their greatest point of expansion. A preventing means I35 on the operating member holds the power lever against movement under the bias of the springs I28 when the operating member is at rest.

When the operating. member is a rest the rear limit of its. travel, as in 3, the springs I28 are fully extended to exert their maximum strength. ihe springs thus. provide a constant ias urging, the reset mechanism to operate. Wheneverv the power lever Ififi is relieved of the holding influence of the preventing means I35 the lever isv free to swing forwardly and operate the reset mechanism through the tractor link connection I23 with the throw link IE3. For the purposes of this specification, and in the claims, the term reset mechanism includes the spring motor means E28 and the power lever IZII as wellvv as the tractor link I23 the throw link its.

"Ifhe preventing means I35 comprises a block that ispi-votally mounted. on the operating meme her to swing in a horizontal plane. The block is adapted for vertical as well. as rotary movementrelative to thecperating member, as shown in Fig. 7..v The block is attached to the lower free end of a stern I39 that is freely rotatable well as vertically slidable in the axial bore of a vertical cylindrical casing I3? that isscrew threaded at its lower end into the body of the operating member; An expansion spring I 38 between the upper end of the stem and the upper closed end of the. casing provides a bias constan-tly urging the block I35 downward toward contact with the. base plate B of' the machine. The block I35 has a beveled face ltd along one side edge thereof. When the operating member is at rest, the preventing means block I35 normally is swung to a position at right angles with respect to the operating member so that it is in contact with a rounded heel flange Mi) on the power lever I29. In this position the heel of the power lever contacts the block I35 at a point between the pivotal axis of the block and the forward end thereof, so that the bias of the power lever tends to rock the preventing block to swing its rear end counterclockwise, so that the power lever is free to move forwardly under the urge of its biasing springs I28. Normally this swinging movement of the preventing block I35 is resisted by blocking means Idi, when the operating member is at rest at the conclusion of a cycle. This blocking means is here shown as a vertical plate having a lateral boss i 32 extending from one face thereof and which pivots on a vertical pint-1e I43 mounted on a Support Hi4 secured between the support plate S and the adjacent side wall 443 of the calculating unit frame. The blockin plate MI is thus pivoted for rocking movement in a horizontal plane. The forward end of the plate has a bottom flange i135 disposed in the path of swing of the preventing member I 35. A biasing spring I46 connected between the rear end portion of the blocking plate and the adjacent side wall of the calculating unit frame urges the plate to a normal position in which it blocks swinging movement of the member I35 in response to the biasing action of the power lever. An inclined finger I41 directed laterally from the rear end portion of the blocking plate provides an abutment engageable with the adjacent side wall of the calculating unit frame to limit pivotal movement of the plate and dispose it in blocking position relative to the preventing member I35.

Whenever the machine is cycled the operating member moves forward in the first half of its cycle. A slight initial portion of this movement is utilized to advance the pivotal axis of the member I35 forwardly with respect to the heel I48 on the power lever. As the operating member goes forward the axis of the member 135 passes ahead of the heel of the power lever and the heel then exerts its force against that portion of the member I35 between its pivotal axis and its rear end. This occurs at the same time that the preventing member 555 is moving with the operating member forwardly beyond control by the blocking plate Idi. Accordingly, as indicated by the dotted line positions in Fig. 3, the preventing member I55 pivots around the heel of the power lever to bring its entire adjacent flat side edge into contact with the straight forward edge of the heel flange Mil on the power lever. In this position the member I35 has shifted from a preventing function to a restraining function. In its restraining function it serves to restrict forward swing of the power lever to the speed of the operating member, so that the power lever cannot swing forwardly with a snap action. Thus the reset mechanism is operated at a speed determined by the speed of the operating member. A pneumatic dash pot his between the intermediate lever isil and a point of attachment on the base plate of the machine provides a brake which retards action of the leverage so that it cannot be operated too rapidly.

As soon as the operating frame has moved forward to the point at which the influence of the member I35 chan es from prevention to restraint, the full force of the springs I28 pulls on the end of the intermediate lever I33 to swing the shiftable fulcrum I32 counterclockwise in a forward arc of movement that is correspondingly transmitted to the power lever I20 and through the tractor link I23 to the throw link I83 for operation of the reset mechanism. When the operating member arrives at its forward limit, as shown in dotted line position in Fig. 4, the reset mechanism will have been fully operated to move the restore bars I01 and II 2 to the positions indicated in Fig. 6, with the racks and rack rests restored to normal non-transfer-receiving position. When the operating member moves rearwardly in the second half of its cycle, the member I35 carries back with it the power lever I20. In it return movement the member I35 swings reversely around the nose flange of the power lever back to its original position into engagement with the blocking plate. movement the operating member, acting through the member I35, provides the motive force for returning the reset mechanism to its original position against the bias of the springs I28. This operation returns the reset bars Iiil and I I2 to their normal free position, as shown in Fig. 5.

The maximum load on the reset mechanism occurs during the last portion of its operation, when the bars Iii! and I I2 engage the rack rests and the racks. This point of engagement occurs in approximately the third quarter of the arc of movement of the reset bars, and the resistance of the load increases to a maximum when the reset is fully operated. Accordingly, the greatest load to be overcome by contraction of the springs I28 occurs during the period at which the springs are nearing their weakest state. The provision of the intermediate lever tee in conjunction with the swinging fulcrum member I33 provides a power amplifying leverage which increases the eifective power of the springs as their contracting power decreases, so that the effective power of the springs actually is at maximum. when the strength of the springs is weakest. This operation is readily understandable from the schematic representation of Fig. 9. In this view the respective starting positions of the power lever, the intermediate lever, and the fulcrum connecting the intermediate lever and the shiftable fulcrum member are indicated by their respective reference characters hereinbefore given. The SllfilX (1 denotes the positions of the parts at the conclusion of the first quarter of the arc of movement; the suiiix 23 indicates the position at the end of the second quarter; the suifix 0 indicates the position at the endof the third quarter, and the suffix d indicates final position at the ccnclusion of the operating movement through the last quarter. Curved line a:.r denotes the path of travel of the shifting fulcrum E32, and the points :cy denote the direction of force exerted by the springs i28. It will be seen that during the first 25% of operation of the reset mechanism the springs contract through approximately 5% of their contracting movement, when they are strongest. During the second 25% of operation of the reset mechanism the springs contract through approximately 17% of their movement. During the third 25% of operating movement of the reset mechanism the springs contract through approximately 29% of their movement. During the last 25% of operation of the reset mechanism the springs are contracting through approximately 48% of their movement. By this arrangement, the greatest contracting movement of the springs takes place in the final quarter of operation of the reset mechanism. Although the In this return 11 are at their weakest strength during this portion of movement, the amplifying power the leverage actually increases the effective force of the springs so that their effective force for purposes of operating the reset mechanism is greatest in the last quarter of its operation.

This invention incorporates means for effecting operation of the reset mechanism independently of movement of the operating member, thereby eliminating the necessity of an enforced blank cycle prior to taking a total. This means includes a control element H59, here shown as a rod axially movable by operation of the total or subtotal key, and which has rigidly secured thereon a cam we. The cam has a tip I55 and an inclined edge i532. In the normal position of parts. prior to an actuation of the total key, the inclined edge of the cam is engaged behind a flange 53 on the short arm I54 of a bell crank lever i555. The bell crank lever is disposed horizontally and is fulcrurned on a stud shaft H56 that is anchored in an element I51 of the machine frame. An expansion spring I53 surrounds the fulcrum shaft between the frame element Isl and a retainer nut 59 on the lower end of the shaft and. maintains the bell crank lever in proper horisontal position. A long arm I651 of the bell crank lever has pivotal connection IiiI at its outer end with a throw link M2 which is in operative connection with a lateral stud I63 on the upper end of the rocker post 2t. When the total key rod its is shifted by actuation of the total key, the rod moves rearwardly, to the right with respect to Fig. 3, whereby the inclined edge I52 of the cam, acting against the rear of the flange 553 on the bell crank rocker, rocks the bell crank lever in a counterclockwise direction. This movement of the bell crank lever is transmitted through the link 562 to actuate the rocker post 2d to the dotted line position of Fig. l, to disengage the register pinions from mesh with their racks. When the cam I553 has advanced to the point at which its inclined edge 552 clears the "flange I53 of the bell. crank lever, the bell crank lever is conditioned for return movement to engage its flange E53 behind a shoulder its on the cam, as shown in Fig. l. This engagement of the flange and cam shoulder latches the rod I4 9 in its fully actuated position.

As the total rod M9 moves rearwardly to cam the bell crank lever I55 for disengagement of the register pinions it carrieswith it an upwardly and laterally directed actuator I65 that is fixedly secured to the shank of the total rod. The ac-' tuator carries an arm I66 pivoted thereon at I6? that is retained in longitudinal alignment with the actuator by means of a contractile spring M3 connected between a flange I69 on the arm and a stud ill) on the actuator. This arrangement permits a counterclockwise movement of the arm l63 relative to the actuator against the force of the biasing spring. As the actuator I65 moves rearwardly with the rod I49, its arm I66 contacts a lateral stud ill on a horizontally disposed interponent lever H2. The forward end of the interponent 8'12 is enlarged to provide a head I13 having a closed end slot I'M that is received over a lateral stud H on the long arm I68 of the bell crank lever i555. The stud and slot connection pulls the interponent forwardly when the bell crank lever is rocked to disengage the register pinions. In moving forward, the stud ill on the interponent cams the pivoted arm I56 to rock against the tension of its spring I68. Forward movement of the interponent advances a shouldered recess lit in the edge of the interponent adjacent its rear end. In its advanced position the recess is adapted to engage the upper end portion ll! of a rod Ilt. The upper portion of this rod is provided with a laterally directed terminal Il s which overlies the interponent. A contractile spring I86 between the support plate S and the shank of the interponent normally biases the interponent to move laterally for engagement of the upper end of the rod Ill in the recess [16.

As soon as the inclined edge H52 on the total rod cam passes forwardly of the bell crank lever flange I53, the force of the tensioned spring I68 acts to rock the arm I66 rearwardly to carry with it the interponent Il2. This movement of the interponent exerts a pull on the bell crank lever stud I75 and this pull snaps the bell crank lever back to a position in which its flange Iii-3 latches behind the shoulder it of the total rod cam, returning link I652 to position shown in Fig. 1, Where stud ltd can oscillate with rocker post 28, in the slot of link I52. Further movement of the bell crank lever is prevented by a retaining flange Isl on the body of the cam. By this means the actuated total key rod M9 is latched in fully actuated position and the total key is held latched until suitable means, not shown, actuated by the operating member when it moves rearward in its last half cycle releases the latch by a vertical lift of lever arm its and flange I53 against the bias of its spring I53, so that the total key may be returned to its non-actuated position.

When the interponent Ilt shifts rearwardly under the pull of the spring its the shoulder at the forward edge of the recess Ill; correspondingly effects a bodily rearward shift of the rod Illl. A guide member I82, attached to a support element I 53 of the machine, is formed with a pair of spaced parallel arms I8 l which straddle the rod and determine the extent of its shifting movement. The lower end of the rod I73 is rigidly secured to the release lever I at. This release lever is inclined rearwardly and downwardly and is pivoted at. its upper end as at I88 to the support I83. By this arrangement, when the rod I78 is rocked rearwardly it rocks the release lever I8! downwardly to lower its rear end extension, a laterally directed rod I89, below the plane of the rear portion of the blocking plate Ill. The extension I69 normally abuts the blocking plate i lI when the release lever is in its normal upper position, as in Figs. 1 and 3. In this upper position the rod holds the blocking plate MI against pivotal movement under the bias of the preventing member I35 which, as previously explained, is itself biased to swing by its engagement with the heel flange Mil on the power lever its. When the release lever it! is rocked downwardly to clear the blocking plate Ml, this plate is free to swing under the force of the preventing member I35, whereupon the preventing member swings, as previously described, to release the heel of the power lever Hill for operation of the reset mechanism.

When the heel of the power lever clears the preventing member 2'5, a relatively weak contractile spring I96 Fig. 8 swings the preventing member out of its transverse position and into alignment with the operating member upon which it is mounted. When in this position, the bevel face E39 of the preventing member is presented forwardly. As the operating member moves into its forward limit position toward the end of the first half cycle, the bevel I39 rides up a complemental inclined face portion 19! on the rear edge of the heel of the power lover. The preventin member thereupon rides up and over the heel of the power lever and drops into position for engagement with the forward edge portion of the heel as shown in dotted line position in Fig. 4. When in this position, the flat side edge of the preventing member contacts 'th'e'heel of the power lever so that when the operating member moves rearwardly in the second half of its cycle the preventing member carries the power lever back with it to return the reset mechanism to its initial condition. In its return movement the member I 35 swings around the nose of the power lever, so that in the last portion of the second half cycle movement of the operating member, just before it comes to rest, the pivotal axis of the member I35 passes rearwardly of the heel flange of the power lever, whereupon the member I35 is swung to its preventin position under the control of the blocking plate I 4| which is held against swinging movement by contact with the end of laterally directed rod I89.

The power lever has associated therewith a motor clutch trip lever I 92 that is pivoted on the fulcrum I2I of the power lever. A contractile spring I93 connected between the shank of the power lever and the rear end of the clutch trip lever provides a yieldable connection urging the clutch trip lever to follow movement of the power lever when the power lever is swung forwardly in the operation of the reset mechanism. When the power lever reaches full operated position, as in Fig. 4, the trip lever I92 will have been moved to the point at which the motor clutch, not shown, is tripped to effect a cycle of the operating member. When the operating member nears the rear limit of its travel on the return stroke it is highly desirable that it be relieved of load wherever possible, so that the motor clutch may be disengaged just slightly before the operating member comes to rest. This relief is effected in this invention by the reverse action of the springs and the amplifying power leverage. The amplifying leverage operates reversely when the power lever returns to normal position so that the heel of the power lever bears only lightly against the preventing member I35, and. the power lever is not given any further rearward movement when the preventing member I35 has swung around the heel I49 and moved rearwardly in contact with flange I45 of blocking plate it. There is, accordingly, only a very slight friction between the heel of the power lever and the preventing member I35 and no further movement of the power lever I29, which materially lightens the load on the operating member when it is moving into its extreme rear limit position.

It will be apparent that the operation of the interponent I72 to disengage the rod I89 from the blocking plate MI is under the control of the bell crank latch lever I55. The interponent cannot move rearwardly to effect release of the plate I 4! until the bell crank lever is in latched position. It is therefore necessary that the total key rod I 49 be moved to its full operated posi tion and that it be latched in that position before the reset mechanism can operate.

When the bell crank lever I 55 is in position holding the rod I49 latched, the interponent lever I12 is held in its rear position, as in Fig. 4, with the upper portion of the rod I18 engaged behind the shoulder of the recess I16. Means is provided for camming the interponent laterally ISO to release 'the rod I18 when the operating mem-- ber goesforward. This means comprises a horizontal lever I94 pivoted at one end to a block I95 secured on the support S. The lever is biased to swing forwardly by the pull of a contractile spring I96 connected between'the lever and guide arm I84. The lever I94 underlies the rear end of the interponent I12 and carries an upstanding stud I91 which is adapted to engage an inclined cam edge I93 of the interponent. A post I99 on the operating member engages the free end of the lever I95 and holds it against forward swing while the operating member is at rest. As the operating member goes forward the post I99 moves ahead of the end of lever I94, which tien swings under the pull of its spring to engage its stud I3! against the cam I98; whereupon the interponent is shifted laterally to release the upper'portion ill of the rod I'IS. Upon release, the rod returns to normal position under pull of a spring I86 connected between the rod I78 and the post I83 at a point well above the pivot of therelease lever I81. Return movement of the rod H8 lifts the release lever into position to reengage the blocking plate I45. When the operating member nears the end of its back stroke the post I99 rcengages the end of the lever I94 and returns the lever to its normal position with the stud I9! disengaged from the interponent :cam I98.

Operation of the reset mechanism by actuation of the total key is effected independently of operating member control. The reset operation is accomplished before the motor clutch is tripped to cycle the operating member. The motive power of the operating member returning in its second half cycle is utilized to restore the reset mechanism to its initial condition and also to return the total key control mechanism to its original condition. When the machine is cycled in taking a total, forward movement of the operating member rocks the post 2% to reengage the register pinions with their racks just before the racks begin their forward stroke from their reset position.

This invention also includes means whereby, in the event of lagging or failure of the springs I23 for any reason, the reset mechanism is operated by a positive drive from the operating member as it arrives at the'end of its forward stroke. This means comprises .a link 2M attached at its forward end to the operating member and extending rearwardly over the yoke I24 and the cross bar IM. A pin 29! on the yoke plays in a longitudinal closed end slot 292 in the link. When the operating member goes forward, the rear end of the .slot normally engages the yoke pin 2Ill as the operating member nears its forward limit position and functions in conjunction with the power lever I29 to operate the reset mechanism. If for any reason the power lever lags or fails to move, the rear end of the link slot 292 picks up the yoke pin at whatever position it oc-- cupies when reached, and propels it forwardly to operate the reset mechanism. This arrangement insures operation of the reset mechanism at each cycle of the operating member. It provides two instrumentalities, acting separately or in unison, for operating the reset mechanism, so that whichever of the two works the faster provides the operating power.

From the detailed description above given, it will be evident that this invention broadly provides a means capable of actuation by the total or sub-total key to effect resetting of racks and rack rests prior to a cycle of the operating member. The reset mechanism, although adapted for positive operation by the operating member, 1s powered to operate independently of control by the operating member, and is biased to operate at al1 times'when the operating member is at rest. Preventing means normally holds the reset mechanism against operation. The holding influence of the preventing means is removable either by cycling the operating member or by actuating the total key prior to a cycle of the operating member. The preventing means is movable on and with the operating member, and when the operating member is at rest the preventing means is engaged with an element of the reset mechanism that is biased to move the preventing means out of its holding position. A blocking means under the control of the total key normally blocks releasing movement of the preventing means while the operating member is at rest. When the reset mechanism is operated by control from the operating member the preventing means has a dual function: it functions first to hold the reset mechanism against operation until the operating member has accomplished an initial portion of its movement, and its functions thereafter during the first half cycle movement of the operating member as a restraining means which limits operation of the reset mechanism to the speed of operation of the operating member. Following either mode of operation of the reset mechanism, restoration of the reset mechanism to initial condition is accomplished by the motive power of the operating member returning through the second half of its cycle.

A broad phase of the reset mechanism includes two restoring elements, the bars I81 and I 52, that are adapted for operation in unison. Either of these elements alone is capable of returning the racks to reset position; and therefore the rack resetting is taken over by whichever of the two moves the faster, thus insuring maximum speed in resetting the racks.

In a further aspect the invention broadly provides a means for utilizing the energy of the operating member moving in its return stroke during its second half cycle to restore the power of the springs which motor the reset mechanism for operation during the forward stroke of the operating member in its first half cycle. In calculating machines in which the type bararegister accumulator actuators, and racks are moved and positioned by springs which are energized by the operating member in the first half of its cycle, it is desirable to use the power of the operating member in the second half of its cycle to energize the reset mechanism. This effects a more even distribution of the motor power driving the operating member, so that it is substantially uniform throughout the full cycle.

The invention also provides broadly an ar-- rangement in which a power lever, driven independently of the machine operating member and movable in a cycle corresponding to the cycle of the operating member, actuates a rack reset mechanism during a part of its first half cycle movement, and is then adapted for positive drive by the operating member during the remainder of its first half cycle to actuate a reset mechanism which restores the rack rests to initial position. The rest reset thus takes place jointly with and following the rack reset.

In another broad phase, the invention provides a power amplifying system in which a spring motored work-performing member is increased in power as it decelerates in movement with increase in load. It provides means for increasing the effective power or" a tensioned spring coincident with decrease in its operating power as it returns to a normal condition of less tension.

The term tens transfer is widely used by the industry and herein to indicate transfer whether carried out at the zero or ten position or whether carried out at other positions such as the eightor twelve position.

Although the present invention has been desc'ibed in conjunction with preferred embodiments, it is to be understood that modifications and variations may be resorted to without departing from the spirit and scope of the invention, as those skilled in the art will readily understand. Such modifications and variations are considered to be within'the purview and scope of the invention and appended claims.

I claim:

1. In a calculating machine, a spring operated tens transfer reset mechanism for returning to normal position all racks and rack rests moved therefrom in eifecting transfers, an operating member for the machine, said reset mechanism being adapted for normal operation under control of the operating member, a control element movable to an actuated position to condition the machine for taking a total, means for latching said control element in actuated position, and means controlled by the latching means to effect operation of the reset mechanism independently of the operating member.

2. In a calculating machine having tens transfer elements and a tens transfer reset mechanism for restoring the tens transfer elements when operated, a cycling operating member, means operativeiy engaging the tens transfer mechanism to bias same to operate independently of the operating member, preventing means on the operating member normally holding the reset mechanism against operation while the operating member is at rest, said preventing means movable with the operating member and becoming ineffective during the first part of the cycle of the operating member to release the tens transfer reset mechanism for operation and becoming eifective during the last portion of the cycle of the operating member to cause return of the tens transfer reset mechanism to its original biased condition.

3. in a calculating machine having tens transfer eiements operative to effect tens transfer during a cycle of operation and tens transfer reset mechanism operatively engaging the tens transfer elements to restore same when operated, a cycling operating member, means biasing the tens transfer reset mechanism to operate independently of the operating member, preventing means carried by the operating member and movable thereon, said preventin means contact ing an eiement of the reset mechanism when the operating member is at rest whereby to hold the reset mechanism against operation, said preventing means being movable by the biasing force of the reset mechanism to release the contacting reset element for operation of the reset mechanism upon initial movement of the operating member from its position of rest, means normally engageable with said preventing means to block its reset release movement, and control means operative to remove the blockin means relative to said preventing means independent of movement of the cycling member from its position of rest.

' 4. In a calculating machine having racks movable from a normal rest position in effecting a transfer, an operating member movable through a cycle, and reset mechanism for restoring to normal position all racks moved therefrom in a transfer; said reset mechanism being adapted for actuation under control of the operating member on each cycle thereof, a control element movable to condition the machine for a total taking operation, and means operative from said control element upon movement thereof to effect actuation of the reset mechanism independently of operating member control.

5. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism biased to operate, means on the operating member normally blocking operation of the tens transfer reset mechanism while the operating member is at rest in its normal position, other means independent of the operating member for rendering said blocking means ineffective to enable the tens transfer reset mechanism to carry out its tens transfer resetting operations.

6. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism biased to operate, means movably mounted on said operating member for operative engagement with said tens transfer reset mechanism to block operation thereof when said operating member is in normal position of rest, said means becoming inoperative upon movement of said operating member through the first portion of its operating cycle, and other means for rendering said blocking means ineffective independent of the operating member.

7. In a calculating machine, a cycling operating member, tens transfer reset mechanism, sprin means constantly urging the reset mechanism to operate while the operating member is in normal position of adjustment, means normally holding the tens transfer reset mechanism against operation while the operating member is in normal position of adjustment, said holding means becoming inefiective during the first portion of the cycle of the operating member and other means for rendering said holding means ineffective independent of said operating member to permit operation of said tens transfer reset mechanism when the operating member is in normal position.

8. In a calculating machine, a cycling operating member, tens transfer reset mechanism, spring means constantly urging the reset mechanism to operate when in the normal position of adjustment, means normally holding the reset mechanism against operation when the cycling member is in normal position of adjustment, said holding means becoming ineffective upon operation of the cycling member, other means for rendering said holding means ineffective independent of said operating member to permit operation of said tens transfer reset mechanism, and means under the control of the operating member to return the spring operated tens transfer reset mechanism to initial condition during the latter portion of its cycle independent of the manner in which the tens transfer reset mechanism was released from its blocked position.

' 9. In a calculating machine, an operating member movable through a cycle of operation upon each operation of the machine, a tens transfer reset mechanism biased to operate, means mounted on the operating member operatively engaging said tens transfer reset mechanism to block operation thereof when the operating member is at rest in its normal position, said blocking means being shiftable with said operating member to release said tens transfer reset mechanism during initial movement of the operating memher through its cycle of operations.

10. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, tens transfer reset mechanism biased to operate, means mounted on the operating member for relative movement and positioned thereon operatively to engage said tens transfer reset mechanism to block operation thereof when said operating member is at rest in its normal position, said blocking means moving out of blockini position during initial movement of the operating member through its cycle of operation to release said tens transfer reset mechanism for operation.

11. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, tens transfer reset mechanism biased to operate, means pivotally mounted on the operating member operatively engaging said tens transfer reset mechanism for blocking movement thereof when said operating member is at rest in its normal position, said blocking means pivoting out of blocking position to release said tens transfer reset mechanism during initial movement of the operating member through its cycle of operation to release said tens transfer reset mechanism for operation.

12. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, tens transfer reset mechanism biased to operate, means pivotally mounted on the operating member operatively engaging said tens transfer reset mechanism for blocking movement thereof when said operating member is at rest in its normal position, said blocking means pivotin to engage said tens transfer reset mechanism from another direction during initial movement of the operating member to release said tens transfer reset mechanism for operation and control movement thereof.

13. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism including a reset lever spring urged to operate, a pawl pivotally mounted on the operating member for operative engagement with the end portion of said lever to block operation thereof when said operating member is in normal position of rest, said pawl shifting out of blocking position upon movement of the operating member in an initial portion of its operating cycle to release said lever for operation of said tens transfer reset mechanism, the pawl continuing operatively to engage the lever for control of the movement of the reset mechanism and return thereof to starting position during return movement of the operating member.

14. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism spring biased to operate, means pivotally mounted on the operatin member operatively engaging the tens transfer reset mechanism for blocking movement thereof when the operating member is in normal position of rest, said blocking means pivoting out of blocking position during initial movement of the operating member to release said tens transfer mechanism for operation, and separate means for pivoting said blocking means out of blocking position while the operating member remains in position of rest to release said tens transfer mechanism in advance of movement of the operating member.

15. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism spring biased to operate, a blocking member mounted for movement relative to the operating member and positioned operatively to engage the tens transfer reset mechanism to prevent operation thereof when the operating member is in normal position of rest, means holding said blocking member in position to block movement of the tens transfer reset mechanism, means pivoting said blockin member out of position for blocking said tens transfer reset mechanism during initial movement of the operating member in its cycle of operation and separate means for rendering said holding means ineffective to release said blocking means independent of movement of said operating member whereby the tens transfer reset mechanism is released for operation.

16. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism spring biased to operate, a blocking member mounted on the operatingmember for movement relative thereto and in position operatively to engage the tens transfer reset mechanism for blocking operation thereof when the operating member is in normal position of rest, means holding said blocking member in position to resist movement of said tens transfer reset mechanism when the operating member is in normal position of rest, said holding means becoming ineffective when said operating member moves out of position of rest during an initial portion of its operating cycle to release said tens transfer reset mechanism for operation, and means for rendering said holding means ineffective whereby the blocking means is released to permit operation of said tens transfer reset mechanism independent of movement of the operating member.

1'7. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism spring biased to operate, a blocking member movably mounted on the operating member, means holding said blocking member in position operatively to engage the tens transfer reset mechanism to block operation thereof when the operating member is in normal position of rest, said holding means becoming ineffective upon movement of the operating member from its position of rest during an initial portion of its operating cycle whereby the blocking member is shifted out of blocking position responsive to the bias of the tens transfer reset mechanism to permit operation thereof, and other means for rendering said holdingmeans ineffective independent of said operating member to release said tens transfer reset mechanism for operation.

18. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, a tens transfer reset mechanism spring biased to operate, a blocking pawl pivotally mounted on the operating member, means holding said pawl in position operatively to engage a portion offset from its pivot with the tens transfer reset mechanism to block oper-. ation thereof when said operating member is in' normal position of rest, said holding means becoming ineffective upon movement of said operating member from its normal position of rest whereby the blocking pawl is pivoted out of blocking position responsive to the biased tens transfer reset mechanism to permit operation thereof, and other means for rendering said holding means ineffective independent of said operating member to permit pivotal movement of said pawl out of blocking position to release said tens transfer mechanism for operation.

19. A calculatin machine as claimed in claim 18 in which said pawl remains in the path of the tens transfer reset mechanism when pivoted out of blocking position upon movement of operating member in its cycle of operation thereby, to control movement of the biased tens transfer reset mechanism during the first half portion of its cycle.

20. A calculating machine as claimed in claim 18 in which the pawl pivots to one side in the path of the biased tens transfer reset mechanism upon release responsive to movement of the operating member from its position of rest and is pivoted to the other side thereof responsive to the offset engagement between the pawl and the biased tens transfer reset mechanism when released from means independent of movement of the operating member.

21. A calculating machine as claimed in claim 18 in which the pawl becomes positioned operatively to engage the tens transfer reset mechanism during the return portion of the cycle of the operatin member no matter how it is released to actuate the tens transfer mechanism to its original biased position with the pawl in its original blocking engagement therewith.

22. In a calculating machine, an operating member movable through a cycle upon each operation of the machine, tens transfer reset mechanism biased to operate, means on the operating member shiftable between a position blocking operation of the tens transfer reset mechanism when the operating member is in normal position of rest and positions releasing said tens transfer reset mechanism for operation, a holder shiftable between position for holding the blocking member in blocking position and for releasing said blocking member for shiftin movement to position releasing said tens transfer reset mechanism for operation, a control member shiftable to a position for conditioning the machine for total taking, latching mechanism in operative engagement with said control member to lock same when actuated to position for total taking, and trip mechanism operated by said control member when locked in position for total taking for shifting said holder to position for release of said means on the operating member from its blocking position.

2;. A calculating machine as claimed in claim 22 in which the means for locking the control member when shifted into position for total taking comprises a cam member shiftable with said control member and having a recess to one side therein, a pivoted lever havin a locking pawl urged in a direction into contact with said cam member whereby the lever is cammed in the other direction until the control member is shifted to position for total taking whereby the slotted portion becomes aligned with said pawl to permit entrance thereof to prevent return of the control member.

24. A calculating machine as claimed in claim 22, in which the trip mechanism comprises a yieldable lever secured to the control member for shifting movement therewith, an interponent movable to control operation of the holder, means responsive to movement of the control member to position for total taking for releasing the interponent for shifting movement between untripped and tripped position of the holder memher, and means responsive to shifting movement of the lever for actuating said interponent towards tripped. position when the control member is locked in position for total taking.

CHARLES A. PARKER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date Muller Feb. 9, Sundstrand July 10, Dreher Feb. 24, Brand Jan. 5, Sundstrand Jan. 26, Svoboda Feb. 26, Mehan Nov. 12, Lornitzo et a1 Oct. 19, 

